US9085982B2 - Gas turbine - Google Patents
Gas turbine Download PDFInfo
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- US9085982B2 US9085982B2 US13/663,579 US201213663579A US9085982B2 US 9085982 B2 US9085982 B2 US 9085982B2 US 201213663579 A US201213663579 A US 201213663579A US 9085982 B2 US9085982 B2 US 9085982B2
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- Prior art keywords
- blade ring
- channel
- tube
- circumferential direction
- steam
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/08—Heating, heat-insulating or cooling means
- F01D5/081—Cooling fluid being directed on the side of the rotor disc or at the roots of the blades
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/12—Cooling of plants
- F02C7/16—Cooling of plants characterised by cooling medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/205—Cooling fluid recirculation, i.e. after cooling one or more components is the cooling fluid recovered and used elsewhere for other purposes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
- F05D2260/2322—Heat transfer, e.g. cooling characterized by the cooling medium steam
Definitions
- the present invention relates to a gas turbine in which a channel through which a cooling medium such as cooling steam is flowed is provided in a blade ring.
- a blade ring thermally expands due to the high temperature combustion gas flowing thereinside, and clearance between the blade ring and the tips of blades is easily increased.
- the increase of clearance is undesirable in terms of stably maintaining the performance of the gas turbine.
- a channel through which cooling steam (cooling medium) is flowed is provided in the blade ring, and thermal expansion of the blade ring is suppressed (for example, refer to Patent Documents 1 and 2 below).
- a plurality of combustors are arranged in the circumferential direction in the upstream side in the turbine shaft direction of the blade ring. The combustors are also cooled using the cooling steam passing through the blade ring.
- an inner channel and an outer channel are provided as the channel of the cooling steam of the blade ring.
- the inner channel is formed in the blade ring.
- the outer channel is connected to the inner channel, is disposed in the outer portion of the blade ring, and is formed in a tubular shape which extends in the circumferential direction of the blade ring.
- the cooling steam performs heat exchange by being flowed through the inner channel and cools the blade ring, and is fed to the combustor and cools the combustor.
- the cooling steam (superheated steam) which has reached high temperature due to the heat exchange with the inner channel and the combustor is mainly recovered through the outer channel so as not to increase the temperature of the blade ring.
- Patent Document 1 Japanese Patent No. 4274666
- Patent Document 2 Japanese Unexamined Patent Application, First Publication No. 2002-309906
- a thermal elongation difference is generated due to a mutual temperature difference between the blade ring and the outer channel which extends in the outer portion of the blade ring.
- high thermal stresses occur in a portion such as a fixing portion through which the outer channel is fixed to the blade ring.
- the present invention is made in consideration of the above-described circumstances, and an object thereof is to provide a gas turbine capable of alleviating thermal stress generated due to a thermal elongation difference between a blade ring and an outer channel thereof.
- the present invention provides the following means.
- a gas turbine includes: a blade ring which faces blades from the outer side in a radial direction perpendicular to a turbine shaft; and a channel provided in the blade ring and through which a cooling medium is flowed, wherein the channel includes: an inner channel formed in the blade ring; and a tubular outer channel which is connected to the inner channel, is disposed in an outer portion of the blade ring, and extends in a circumferential direction of the blade ring, and the outer channel includes: a plurality of fixing portions fixed to the blade ring; and a thermal stress absorbing portion which is disposed between the fixing portions adjacent in the circumferential direction and is expandable and contractible in the circumferential direction.
- the blade ring is cooled by flowing a cooling medium such as cooling steam through the channel, and the thermal expansion of the blade ring toward the outer side in the radial direction is suppressed.
- a cooling medium such as cooling steam
- the cooling medium performs heat exchange by being flowed through the inner channel and cools the blade ring.
- the cooling medium which has reached high temperature due to the heat exchange is recovered through the outer channel so as not to increase the temperature of the blade ring.
- the outer channel includes the thermal stress absorbing portion which is expandable in the circumferential direction between fixing portions adjacent in the circumferential direction, the following effects are exhibited.
- the thermal stress absorbing portion expands and contracts, and thus, the thermal elongation difference can be absorbed, and thermal stress is decreased.
- the thermal stress absorbing portion of the gas turbine may be a bellows tube.
- the thermal stress absorbing portion can be simply manufactured.
- the thermal stress absorbing portion of the gas turbine may be a tube bent so as to be folded in a direction crossing the circumferential direction.
- the tube bent so as to be folded in the direction crossing the circumferential direction bends in the circumferential direction (that is, expands and contracts in the circumferential direction as a thermal stress absorbing portion), and thus, the thermal stress is decreased.
- the gas turbine of the present invention it is possible to alleviate the thermal stress generated due to the thermal elongation difference between the blade ring and the outer channel thereof.
- FIG. 1 is a system diagram of a cooling medium of a blade ring of a gas turbine according to a first embodiment of the present invention.
- FIG. 2 is a front view when the blade ring of the gas turbine according to the first embodiment of the present invention is viewed from the direction of a turbine shaft.
- FIG. 3 is a top view when the blade ring of the gas turbine according to the first embodiment of the present invention is viewed from the radial direction.
- FIG. 4 is a view explaining an outer channel for supplying steam in the blade ring of FIG. 2 .
- FIG. 5 is a view explaining an outer channel for discharging steam in the blade ring of FIG. 2 .
- FIG. 6 is a view explaining an outer channel for supplying steam according to a second embodiment.
- FIG. 7 is a view explaining an outer channel for discharging steam according to the second embodiment.
- a gas turbine mixes compressed air generated in a compressor with a fuel and combusts the mixture in a combustor, and generates high temperature and high pressure combustion gas. Moreover, the combustion gas is flowed into the turbine, and thus, a rotor of the turbine is rotated around a turbine shaft C, and rotational power is obtained.
- a plurality of blade rings 1 which are coaxial with the turbine shaft C are disposed in the turbine shaft C direction in the turbine.
- the blade rings 1 support vanes from the outer side in the radial direction.
- the blade ring 1 faces blades adjacent to the vanes in the turbine shaft C direction from the outer side in the radial direction with an interval (clearance) between tips of the blades and the blade ring.
- the compressor side of the combustor along the turbine shaft C direction is referred to as an upstream side, and the turbine side of the combustor is referred to as a downstream side.
- a direction perpendicular to the turbine shaft C direction is referred to as a radial direction, and a direction which rotates around the turbine shaft C is referred to as a circumferential direction.
- the gas turbine of the present embodiment is a gas turbine which cools the blade ring 1 using cooling steam as an example of a cooling medium.
- the gas turbine includes the above-described blade ring 1 and a channel 2 provided in the blade ring 1 and of which the cooling steam is flowed through the inner portion.
- a pair of semi-annular segment bodies is combined, and the entire blade ring 1 is formed in an annular shape.
- a tubular steam supply portion 1 a and steam discharging portion 1 b protrude so that the axes of the portions face the radial direction.
- the cooling steam is supplied from a steam turbine bottoming system to the channel 2 through the steam supply portion 1 a . After the cooling steam cools the blade ring 1 , the cooling steam is returned to the steam turbine bottoming system from the steam discharging portion 1 b.
- the blade ring 1 of the present embodiment is the blade ring 1 which faces a 1st stage blades disposed so as to be close to the combustor. After the cooling steam cools the blade ring 1 , the cooling steam is flowed through the channel of the combustor and cools the combustor. Thereafter, the cooling steam is returned to the steam turbine bottoming system from the channel 2 of the blade ring 1 again.
- FIG. 1 shows a system diagram of cooling steam for a blade ring.
- FIG. 1 shows the cooling system formed in an upper half blade ring 1 m of the blade ring 1 .
- the description of the system in a lower half blade ring 1 n of the blade ring 1 is omitted, the system of the lower half blade ring 1 n is similar to that of the upper half blade ring 1 m .
- the upper half blade ring 1 m is integrated with the lower half blade ring 1 n , and thereby a single blade ring 1 is formed.
- the cooling steam is supplied to the steam supply portion 1 a , which is provided on the upper half blade ring 1 m , as a cooling medium of the blade ring 1 from the steam bottoming system 20 . Meanwhile, after the cooling steam cools the blade ring 1 , the cooling steam is returned to the steam bottoming system 20 from the steam discharging portion 1 b provided on the blade ring 1 .
- a reference numeral 2 A is attached to a steam supply system
- a reference numeral 2 B is attached to a steam return system (steam discharge system), and both systems are distinguished from each other.
- a port 5 which is integrally formed to the blade ring 1 is provided so as to correspond to the position of each combustor for delivery of the cooling steam to each corresponding combustor.
- Each port 5 includes a connection port 5 A which sends the cooling steam to the combustor and a connection port 5 B which receives the cooling steam returned from the combustor.
- FIG. 1 an example in which eight combustors are disposed to the upper half blade ring 1 m is shown.
- the present invention is not limited to the example.
- the cooling steam supplied from the steam supply portion 1 a to the upper half blade ring 1 m is divided into two systems and is flowed to the channel 2 A.
- the cooling steam is supplied to the port 5 while cooling the blade ring 1 m and is supplied to the combustor from the connection port 5 A.
- the cooling steam is supplied to the upper half blade ring 1 m from the connection port 5 B of the port 5 and is returned to the steam discharging portion 1 b via the channel 2 B.
- the channel 2 A which supplies the cooling steam to the connection port 5 A of the port 5 from the steam supply portion 1 a , includes channels 4 A, 6 A, and 7 A described below.
- the channel 2 B in which the cooling steam which is returned from the combustor and is discharged to the steam discharging portion 1 b from the connection port 5 B of the port 5 is flowed, includes channels 4 B, 6 B, and channel 7 B described below.
- the tubular outer channels ( 6 A, 6 B, 7 A, and 7 B) disposed in the outer portion of the blade ring 1 are indicated by a solid line.
- An inner channel 4 ( 4 A and 4 B) indicated by a broken line is disposed in the inner portion of the blade ring 1 between the outer channels and the connection ports 5 A and 5 B of each port 5 , and the blade ring 1 is cooled by the cooling steam.
- classification and combination of the outer channel and the inner channel shown in FIG. 1 are examples, and the present invention is not limited to the examples.
- the channels 2 A and 2 B include inner channels 4 A and 4 B formed in the blade ring 1 , and tubular outer channels 6 A, 6 B, 7 A, and 7 B which are connected to the inner channels 4 A and 4 B, are disposed in the outer portion of the blade ring 1 , and extend in the circumferential direction of the blade ring 1 .
- the port 5 which includes the connection ports 5 A and 5 B which are piping performing delivery of the cooling steam to the combustor is disposed at the position facing each combustor on an end surface 1 c which faces the upstream side in the turbine shaft C direction of the blade ring 1 .
- the connection port 5 A supplies the cooling steam to the channel of the combustor from the inner channel 4 A.
- the connection port 5 B recovers the steam, which performs heat exchange in the inner portion of the combustor after being supplied to the combustor from the connection port 5 A, in the inner channel 4 B from the channel of the combustor.
- the connection ports 5 A and 5 B are opened so as to be adjacent in the circumferential direction.
- the connection ports 5 A and 5 B adjacent to each other are connected to both end portions of the channel of the combustor which face the connection ports 5 A and 5 B.
- the plurality of inner channels 4 are formed with intervals in the circumferential direction in the blade ring 1 .
- the inner channel 4 ( 4 A and 4 B) includes the first inner channel 4 A and the second inner channel 4 B.
- the first inner channel 4 A is a steam supply system through which the steam which cools the blade ring 1 and the combustor is flowed.
- the second inner channel 4 B is a steam discharge system through which the steam, which has been recovered from the combustor and been subjected to the heat exchange, is flowed.
- the first and second inner channels 4 A and 4 B are alternately disposed in the circumferential direction.
- eight pairs of inner channels 4 A and 4 B are formed so as to correspond to the positions of the combustors arranged in the circumferential direction in the segment bodies (upper half blade ring 1 m and lower half blade ring 1 n ) of the blade ring 1 formed in a semi-annular shape.
- the first inner channel 4 A is formed by linking channel portions 41 A which extend in the turbine shaft C direction and a channel portion 42 A which extends in the circumferential direction, and extends so as to be bent in a U shape in the blade ring 1 .
- the first inner channel 4 A is bent in the circumferential direction and extends toward the upstream side so as to be folded again (refer to FIG. 3 for the upstream side and the downstream side in the turbine shaft C direction in the blade ring 1 ).
- the channel portions 41 A which extend in the turbine shaft C direction in the first inner channel 4 A are separated in the circumferential direction and are formed into a pair in each first channel 4 A. All the channel portions 41 A are connected to connection ports 5 A opened to the end surface 1 c of the blade ring 1 .
- the opening portion of one channel portion 41 A (the right channel portion 41 A in FIG. 2 ) to the end surface 1 c is connected to a fixing portion 16 A of the first outer channel ( 6 A and 7 A) described below.
- the opening portion of the other channel portion 41 A (the left channel portion 41 A in FIG. 2 ) disposed in the wake flow side to the end surface 1 c is a connection port 5 A.
- the channel portions 41 A extend parallel to each other along the turbine shaft C direction as shown by a broken line in FIG. 2 .
- the channel portion 42 A which extends in the circumferential direction in the first inner channel 4 A connects end portions of the downstream side in the turbine shaft C direction of the pair of channel portions 41 A in each first inner channel 4 A, and extends in a linear shape or a curve shape.
- the channel portion 42 A is formed in the main body of the blade ring 1 so as to correspond to the pair of channel portions 41 A, and both ends of the channel portion 42 A are connected to the channel portions 41 A.
- the first inner channel 4 A is formed so that the entire length is secured to be long.
- the second inner channel 4 B is formed so that the entire length is as short as possible.
- the outer channel (first outer channel) of the steam supply system is disposed in the outer side in the radial direction of the blade ring 1 and includes a tube portion 6 A and a tube portion 7 A.
- the tube portion 6 A extends along the circumferential direction.
- the tube portion 7 A is branched from the tube portion 6 A and extends along the radial direction, and the end portion of the tube portion 7 A is connected to the first inner channel 4 A of the blade ring 1 .
- the outer channel (second outer channel) of the steam discharge system is disposed in the outer side in the radial direction of the blade ring 1 and includes a tube portion 6 B and a tube portion 7 B.
- the tube portion 6 B extends along the circumferential direction.
- the tube portion 7 B is branched from the tube portion 6 B and extends along the radial direction, and the end portion of the tube portion 7 B is connected to the second inner channel 4 B of the blade ring 1 .
- the tube portion 6 A is connected to the steam supply portion 1 a , and in the shown example, the pair of tube portions 6 A is provided on both sides in the circumferential direction while interposing the steam supply portion 1 a .
- the diameter in the portion connected to the steam supply portion 1 a is the largest.
- the tube diameter of the tube portion 6 A is set so as to be decreased in stages (so as to be decreased in stages whenever crossing the bifurcated portion of tube portion 6 A from the tube portion 7 A) as the tube portion 6 A is separated from the steam supply portion 1 a.
- the end portion 16 A of the inner side in the radial direction of the tube portion 7 A is supported so as to be fixed to the end surface 1 c which faces the upstream side in the turbine shaft C direction in the blade ring 1 .
- the end portion 16 A of the tube portion 7 A is a fixing portion which fixes the first outer channel to the blade ring 1 .
- connection end 13 A to the steam supply portion 1 a in the tube portion 6 A also is a fixing portion which fixes the first outer channel to the blade ring 1 .
- the end portion 14 A of the side opposite to the steam supply portion 1 a of both end portions in the circumferential direction of the one tube portion 6 A is directly fixed to the outer circumferential surface of the blade ring 1 without going through the tube portion 7 A.
- the end portion 14 A also is a fixing portion which fixes the first outer channel to the blade ring 1 .
- the fixing portion of the first outer channel includes the fixing portion provided on the blade ring 1 side, a branch piping coupling 12 A, and a curved piping coupling 15 A.
- the branch piping coupling 12 A branches the channel from the tube portion 6 A to the tube portion 7 A.
- the curved piping coupling 15 A changes the direction of the channel from the tube portion 6 A to the tube portion 7 A.
- the fixing portion provided in the blade ring 1 side includes the connection end 13 A and the end portion 14 A described above.
- the branch piping coupling 12 A connects the tube portion 6 A and the tube portion 7 A in a T shape, and the end portion 16 A in the inner side in the radial direction of the tube portion 7 A is fixed to the blade ring 1 .
- the curved piping coupling 15 A is shown in the left end portion in FIG. 4 , connects the tube portion 6 A and the tube portion 7 A in an L shape, and the end portion 16 A in the inner side in the radial direction of the tube portion 7 A is fixed to the blade ring 1 .
- the shape, the disposition, or the like of the fixing portions of the steam supply system is an example, and the present invention is not limited to the example.
- the first outer channel ( 6 A and 7 A) includes a thermal stress absorbing portion 8 A disposed between fixing portions adjacent in the circumferential direction and is expandable in the circumferential direction.
- the thermal stress absorbing portion 8 A is provided in the tube portion 6 A, and is disposed in an intermediate portion interposed to any of the fixing portion fixed to the blade ring 1 , the branch piping coupling 12 A, and the curved piping coupling 15 A.
- the thermal stress absorbing portion 8 A of the present embodiment has a bellows structure in which the peripheral wall of the tube is formed in a plurality of folds in the radial direction of the tube.
- a bellows tube flexible tube expandable in the circumferential direction of the blade ring 1 can be used.
- the tube diameters of the bellows tubes are set according to the tube diameter of the part of the tube portion 6 A where the bellows tube is disposed respectively, and the tube diameter of the bellows tube close to the steam supply portion 1 a is the largest, and the tube diameter of the bellows tube is decreased in stages according to the tube diameter of the tube portion 6 A as the bellows tube is separated from the steam supply portion 1 a.
- the plurality of second outer channels ( 6 B and 7 B) are disposed in the blade ring 1 , and the second outer channel includes the tube portion 6 B and the tube portion 7 B.
- the tube portion 6 B is disposed in the outer side in the radial direction of the blade ring 1 and extends along the circumferential direction.
- the tube portion 7 B extends along the radial direction, and both ends of the tube portion 7 B are connected to the tube portion 6 B and the second inner channel 4 B of the blade ring 1 .
- the second outer channel ( 6 B and 7 B) is disposed so as to be adjacent to the downstream side (upper side in FIG. 3 ) in the turbine shaft C direction of the first outer channel ( 6 A and 7 A).
- the tube portions 6 B are connected to the steam discharging portion 1 b , and in the shown example, a pair of the tube portions 6 B is provided in both sides in the circumferential direction while interposing each of the pair of steam discharging portions 1 b .
- the tube diameter (inner diameter) of the tube portion 6 B the diameter in the portion connected to the steam discharging portion 1 b is the largest, and the tube diameter of the tube portion 6 B is set so as to be decreased in stages (specifically, so as to be decreased in stages whenever crossing the portion branched from the tube portion 7 B) as the tube portion 6 B is separated from the steam discharging portion 1 b.
- a connection end 13 B to the steam discharging portion 1 b in the tube portion 6 B also is a fixing portion which fixes the second outer channel to the blade ring 1 .
- the end portion 14 B of the side opposite to the steam discharging portion 1 b of both end portions in the circumferential direction of the tube portion 6 B is directly fixed to the outer circumferential surface of the blade ring 1 without going through the tube portion 7 B.
- the end portion 14 B also is a fixing portion which fixes the second outer channel to the blade ring 1 .
- the fixing portion of the second outer channel includes the fixing portion provided on the blade ring 1 side and a branch piping coupling 12 B.
- the branch piping coupling 12 B branches the channel from the tube portion 6 B to the tube portion 7 B.
- the fixing portion provided in the blade ring 1 side includes the connection end 13 B and the end portion 14 B described above.
- the branch piping coupling 12 B connects the tube portion 6 B and the tube portion 7 B in a T shape, and the end portion 16 B in the inner side in the radial direction of the tube portion 7 B is fixed to the blade ring 1 .
- the shape, the disposition, or the like of the fixing portions of the steam discharge system is an example, and the present invention is not limited to the example.
- the second outer channel ( 6 B and 7 B) includes a thermal stress absorbing portion 8 B disposed between fixing portions adjacent in the circumferential direction and is expandable in the circumferential direction.
- the thermal stress absorbing portion 8 B is provided in the tube portion 6 B, and is disposed in an intermediate portion interposed to the fixing portion fixed to the blade ring 1 and the branch piping coupling 12 B.
- the thermal stress absorbing portion 8 B of the present embodiment also can use the bellows tube which has the configuration similar to the above-described thermal stress absorbing portion 8 A.
- the tube diameters of the bellows tubes are set according to the tube diameter of the part of the tube portion 6 B where the bellows tube is disposed respectively, the tube diameter of the bellows tube close to the steam discharging portion 1 b is the largest, and the tube diameter of the bellows tube is decreased in stages according to the tube diameter of the tube portion 6 B as the bellows tube is separated from the steam discharging portion 1 b.
- the blade ring 1 is cooled by circulating the cooling steam through the channel 2 , and the thermal expansion of the blade ring 1 toward the outer side in the radial direction is suppressed. Thereby, an increase of a clearance between the blade ring 1 and the tip of the blade during operation is suppressed, and performance of the gas turbine is stably maintained.
- the cooling steam passes through the first outer channel 6 A from the steam supply portion 1 a and flows to the tube portion 7 A via the branch piping coupling 12 A or the curved piping coupling 15 A. Subsequently, the cooling steam communicates with the first inner channel 4 A, performs heat exchange, and thus, cools the blade ring 1 . In addition, in the end portion 14 A of the tube portion 6 A, the cooling steam communicates with the first inner channel 4 A without going through the tube portion 7 A. Furthermore, the cooling steam flows through the channel of the combustor, performs heat exchange, and thus, cools the combustor. The cooling steam which reaches high temperature by the heat exchange is returned to the blade ring 1 from the combustor.
- the cooling steam passes through the second inner channel 4 B shown in FIG. 5 which has the short entire length, flows to the tube portion 7 B, joins the steam from other system in the branch piping coupling 12 B, passes through the second outer channel 6 B, and is recovered from the steam discharging portion 1 b . Moreover, in the end portion 14 B of the tube portion 6 B, the cooling steam joins the steam from other system without going through the tube portion 7 B.
- the temperature is increased in the order of the first outer channel ( 6 A and 7 A), the blade ring 1 , and the second outer channel ( 6 B and 7 B) (that is, the temperature of the outer channel 6 B is the highest).
- the outer channel ( 6 A, 6 B, 7 A, and 7 B) includes the thermal stress absorbing portions 8 A and 8 B which are expandable in the circumferential direction between fixing portions adjacent in the circumferential direction, the following effects are exhibited.
- the thermal stress absorbing portions 8 A and 8 B expand and contract, and thus, the thermal elongation difference can be absorbed, and thermal stress is decreased.
- the thermal stress occurs in the direction of expanding the first outer channel in the circumferential direction due to the thermal elongation difference between the channel ( 6 A and 7 A) and the blade ring 1 having a higher temperature than the channel ( 6 A and 7 A).
- the thermal stress absorbing portion 8 A provided in the first outer channel ( 6 A and 7 A) expands in the circumferential direction, the thermal stress is decreased.
- the thermal stress absorbing portion 8 B provided in the second outer channel ( 6 B and 7 B) contracts in the circumferential direction, and thus, the thermal stress is decreased.
- thermal stress absorbing portions 8 A and 8 B are configured of the bellows tube, the thermal stress absorbing portions 8 A and 8 B can be simply manufactured.
- the present embodiment is different from the first embodiment in that a tube (hereinafter, referred to as curved tubes 8 A and 8 B) curved so as to be folded in a direction crossing the circumferential direction is used instead of using the bellows tube described above in the first embodiment, and other components are the same as the first embodiment.
- a tube hereinafter, referred to as curved tubes 8 A and 8 B
- curved tubes 8 A and 8 B curved so as to be folded in a direction crossing the circumferential direction
- FIG. 6 shows the outer pipes ( 6 A and 7 A) of a steam supply system and FIG. 7 shows the outer pipes ( 6 B and 7 B) of a steam discharge system.
- the second embodiment is an example in which the curved tube ( 8 A and 8 B) is provided in the center portion of the outer pipe ( 6 A and 6 B) in which both ends are supported by the fixing portion fixed to the blade ring 1 or the branch piping coupling instead of the bellows tube as the thermal stress absorber applied to the first embodiment.
- the bellows tube similar to the first embodiment is disposed.
- Other components are similar to the first embodiment.
- thermal stress absorbing portions 8 A and 8 B are tubes (curved tubes) curved so as to be folded in the direction crossing the circumferential direction, the following operation and effects are obtained.
- thermal stress occurs in the tube portion 6 A in the direction of expanding the tube portion 6 A in the circumferential direction due to the thermal elongation difference between the blade ring 1 and the channel ( 6 A and 7 A).
- the curved tube 8 A of the tube portion 6 A bends in the circumferential direction (that is, expands in the circumferential direction as the thermal stress absorbing portion 8 A), and thus, the thermal stress is decreased.
- the second outer channel ( 6 B and 7 B) has higher temperature than the blade ring 1 , it is considered that thermal stress occurs in the tube portion 6 B in the direction of contracting the tube portion 6 B in the circumferential direction due to the thermal elongation difference between the channel ( 6 B and 7 B) and the blade ring 1 .
- the curved tube 8 B of the tube portion 6 B bends in the circumferential direction (that is, contracts in the circumferential direction as the thermal stress absorbing portion 8 B), and thus, the thermal stress is decreased.
- the curved tube of the present embodiment since the cost is lower than the bellows tube, the curved tube of the present embodiment has advantages in terms of economical efficiency of the gas turbine.
- the above-described embodiments are described using the cooling steam as a cooling medium.
- a cooling medium other than the cooling steam for example, such as air may be used.
- the gas turbine is provided with the blade rings 1 having the channel 2 through which the cooling steam is flowed, wherein the blade rings are aligned in the direction of the turbine shaft C.
- the present invention is not limited thereto, and it is only necessary that at least one such blade ring 1 is provided.
- the cooling steam After the cooling steam cools the blade ring 1 , the cooling steam is flowed through the channel of the combustor and cools the combustor. However, it is only necessary that the cooling steam cools at least the blade ring 1 , and the cooling steam may be recovered without cooling the combustor.
- the one thermal stress absorbing portions 8 A or 8 B is disposed between fixing portions adjacent to each other in the circumferential direction.
- the multiple thermal stress absorbing portions may be disposed between the fixing portions.
- the first outer channel ( 6 A and 7 A) for supplying steam is provided as an inner channel
- the second channel ( 6 B and 7 B) for discharging steam may be provided as an outer pipe.
- the inner channel may be provided instead of the second outer channel ( 6 B and 7 B) for discharging steam.
- the curved tube (the portion between fixing portions adjacent in the circumferential direction of the tube portions 6 A and 6 B or the branch piping couplings) which is the thermal stress absorbing portions 8 A and 8 B is formed so as to be folded in the radial direction.
- the present invention is not limited thereto. That is, it is only necessary that the curved tubes 8 A and 8 B are curved so as to be folded in the direction crossing the circumferential direction, and for example, the curved tubes 8 A and 8 B may be formed so as to be folded in the turbine shaft C direction.
- connection tube connection channel
- connection end fixing portion
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Abstract
Description
Claims (3)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2012-062126 | 2012-03-19 | ||
JP2012062126 | 2012-03-19 |
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US20130243576A1 US20130243576A1 (en) | 2013-09-19 |
US9085982B2 true US9085982B2 (en) | 2015-07-21 |
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US13/663,579 Active 2034-01-02 US9085982B2 (en) | 2012-03-19 | 2012-10-30 | Gas turbine |
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JP (1) | JP5908063B2 (en) |
KR (1) | KR101640334B1 (en) |
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11268445B2 (en) | 2017-05-16 | 2022-03-08 | Mitsubishi Power, Ltd. | Gas turbine and method for blade ring production method |
Families Citing this family (5)
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---|---|---|---|---|
CN105317559B (en) * | 2014-05-29 | 2017-08-04 | 北京航空航天大学 | With support case after the turbine of rectification leaf grating integration connection |
US10378379B2 (en) * | 2015-08-27 | 2019-08-13 | General Electric Company | Gas turbine engine cooling air manifolds with spoolies |
US10113486B2 (en) | 2015-10-06 | 2018-10-30 | General Electric Company | Method and system for modulated turbine cooling |
FR3079874B1 (en) * | 2018-04-09 | 2020-03-13 | Safran Aircraft Engines | COOLING DEVICE FOR A TURBINE OF A TURBOMACHINE |
CN111305905B (en) * | 2020-02-26 | 2021-06-08 | 中国科学院工程热物理研究所 | Cooling structure and method suitable for rich-combustion working medium turbine rotating and static disc cavity |
Citations (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2048386A (en) | 1979-03-28 | 1980-12-10 | United Technologies Corp | Gas turbine compressor construction to promote even cooling |
US5116199A (en) | 1990-12-20 | 1992-05-26 | General Electric Company | Blade tip clearance control apparatus using shroud segment annular support ring thermal expansion |
US5167488A (en) * | 1991-07-03 | 1992-12-01 | General Electric Company | Clearance control assembly having a thermally-controlled one-piece cylindrical housing for radially positioning shroud segments |
US5399066A (en) * | 1993-09-30 | 1995-03-21 | General Electric Company | Integral clearance control impingement manifold and environmental shield |
JPH08215879A (en) | 1995-02-20 | 1996-08-27 | Kawasaki Heavy Ind Ltd | Welded structure of tube and flange connected structure of tube |
US5980201A (en) * | 1996-06-27 | 1999-11-09 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation | Device for blowing gases for regulating clearances in a gas turbine engine |
US6035929A (en) * | 1997-07-18 | 2000-03-14 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation "Snecma" | Apparatus for heating or cooling a circular housing |
JP2000080926A (en) | 1998-09-04 | 2000-03-21 | Hitachi Ltd | Thermal power plant and operating method thereof |
US6185925B1 (en) | 1999-02-12 | 2001-02-13 | General Electric Company | External cooling system for turbine frame |
US6224328B1 (en) | 1998-08-31 | 2001-05-01 | Asea Brown Boveri Ag | Turbomachine with cooled rotor shaft |
US6454529B1 (en) * | 2001-03-23 | 2002-09-24 | General Electric Company | Methods and apparatus for maintaining rotor assembly tip clearances |
JP2002309906A (en) | 2001-04-11 | 2002-10-23 | Mitsubishi Heavy Ind Ltd | Steam cooling type gas turbine |
JP2005188857A (en) | 2003-12-26 | 2005-07-14 | Mitsubishi Heavy Ind Ltd | Main nozzle and combustor |
JP4274666B2 (en) | 2000-03-07 | 2009-06-10 | 三菱重工業株式会社 | gas turbine |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4438625A (en) | 1978-10-26 | 1984-03-27 | Rice Ivan G | Reheat gas turbine combined with steam turbine |
JPH04274666A (en) | 1991-02-28 | 1992-09-30 | Nec Corp | Facsimile transmitter-receiver |
US5584511A (en) | 1995-10-23 | 1996-12-17 | General Electric Company | Multi-degree-of-freedom expansion joint |
DE19926949B4 (en) * | 1999-06-14 | 2011-01-05 | Alstom | Cooling arrangement for blades of a gas turbine |
EP1428001B1 (en) | 2001-09-13 | 2011-01-12 | General Electric Company | Method and apparatus for model based estimation of natural frequency responses of tube sub-systems including shrouded bellows |
-
2012
- 2012-10-30 US US13/663,579 patent/US9085982B2/en active Active
- 2012-10-31 CN CN201280067025.2A patent/CN104053860B/en active Active
- 2012-10-31 WO PCT/JP2012/078110 patent/WO2013140655A1/en active Application Filing
- 2012-10-31 JP JP2014505965A patent/JP5908063B2/en active Active
- 2012-10-31 DE DE112012006059.8T patent/DE112012006059B4/en active Active
- 2012-10-31 KR KR1020147019382A patent/KR101640334B1/en active IP Right Grant
Patent Citations (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2048386A (en) | 1979-03-28 | 1980-12-10 | United Technologies Corp | Gas turbine compressor construction to promote even cooling |
US5116199A (en) | 1990-12-20 | 1992-05-26 | General Electric Company | Blade tip clearance control apparatus using shroud segment annular support ring thermal expansion |
US5167488A (en) * | 1991-07-03 | 1992-12-01 | General Electric Company | Clearance control assembly having a thermally-controlled one-piece cylindrical housing for radially positioning shroud segments |
US5399066A (en) * | 1993-09-30 | 1995-03-21 | General Electric Company | Integral clearance control impingement manifold and environmental shield |
JPH08215879A (en) | 1995-02-20 | 1996-08-27 | Kawasaki Heavy Ind Ltd | Welded structure of tube and flange connected structure of tube |
US5980201A (en) * | 1996-06-27 | 1999-11-09 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation | Device for blowing gases for regulating clearances in a gas turbine engine |
US6035929A (en) * | 1997-07-18 | 2000-03-14 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation "Snecma" | Apparatus for heating or cooling a circular housing |
US6224328B1 (en) | 1998-08-31 | 2001-05-01 | Asea Brown Boveri Ag | Turbomachine with cooled rotor shaft |
JP2000080926A (en) | 1998-09-04 | 2000-03-21 | Hitachi Ltd | Thermal power plant and operating method thereof |
US6185925B1 (en) | 1999-02-12 | 2001-02-13 | General Electric Company | External cooling system for turbine frame |
JP4274666B2 (en) | 2000-03-07 | 2009-06-10 | 三菱重工業株式会社 | gas turbine |
US6454529B1 (en) * | 2001-03-23 | 2002-09-24 | General Electric Company | Methods and apparatus for maintaining rotor assembly tip clearances |
JP2002309907A (en) | 2001-03-23 | 2002-10-23 | General Electric Co <Ge> | Method and device for maintaining gap between tips of rotor assemblies |
JP2002309906A (en) | 2001-04-11 | 2002-10-23 | Mitsubishi Heavy Ind Ltd | Steam cooling type gas turbine |
JP2005188857A (en) | 2003-12-26 | 2005-07-14 | Mitsubishi Heavy Ind Ltd | Main nozzle and combustor |
Non-Patent Citations (4)
Title |
---|
Chinese Office Action dated Mar. 17, 2015, issued in CN Patent Application No. 201280067025.2 with English partial translation (10 pages). |
English translation of the Written Opinion of PCT/JP2012/078110, mailing date of Jan. 29, 2013 (6 pages). |
International Search Report of PCT/JP2012/078110, mailing date of Jan. 29, 2013, w/English tranlsation. |
Written Opinion of PCT/JP2012/078110, mailing date of Jan. 29, 2013. |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11268445B2 (en) | 2017-05-16 | 2022-03-08 | Mitsubishi Power, Ltd. | Gas turbine and method for blade ring production method |
Also Published As
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US20130243576A1 (en) | 2013-09-19 |
KR101640334B1 (en) | 2016-07-15 |
KR20140100576A (en) | 2014-08-14 |
JPWO2013140655A1 (en) | 2015-08-03 |
DE112012006059T5 (en) | 2014-12-04 |
JP5908063B2 (en) | 2016-04-26 |
DE112012006059B4 (en) | 2019-03-14 |
WO2013140655A1 (en) | 2013-09-26 |
CN104053860B (en) | 2016-02-10 |
CN104053860A (en) | 2014-09-17 |
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